Multispeed driving mechanisms



Jan. 22, 1963 G. M. SOMMER ETAL 3,074,297

MULTISPEED DRIVING MECHANISMS Filed Jan. 10, 1958 4 Sheets-Sheet 1 INVENTORSZ GORDON M. SOMMER CHARLES L. MITCHELL VINCENT J. MANKOWSKY z yaw M v gb ATT'YS Jan. 22, 1963 cs. M. SOMMER ETAL 3,074,297

MULTISPEED DRIVING MECHANISMS 4 Sheets-Sheet 2 Filed Jan. 10, 1958 GORDON M. SOMMER CHARLES L. MITCHELL VINCENT J. MANKOWSKY Jan. 22, 1963 G. M. SOMMER ETAL 3,074,297

MULTISPEED DRIVING MECHANISMS Filed Jan. 10, 1958 4 Sheets-Sheet 3 m m m m m N m v m mm m r IO IO n R 7K o I N g I i E O d m S), g m g 8 8 I 9 g; Q 8

as r

m Q r o on Q lg n w I i a to i-t/ I 1 e n l@ l a o: N a

FIG. 4

INVENT DON M. SOMME ATT'YS 1963 G. M. SOMMER ETAL 3,074,297

United States Patent M 3,074,297 MULTISPEED DRIVING MECHANISMS Gordon M. Sommer, Hinsdale, 111., Charles L. Mitchell,

Cincinnati, Ohio, and Vincent J. Mankowsky, Chicago,

111., assignors to US. Industries, Inc., New York, N.Y.,

a corporation of Delaware Filed Jan. 10, 1958, Ser. No. 708,286 11 Claims. (Cl. 74750) This invention relates in general to multispeed driving mechanisms and, more particularly, to driving mechanisms which are particularly well adapted for use in rotating the drive shaft of mechanical metal drawing presses, and the like, at a plurality of selected speeds.

It is a primary object of this invention to alford a novel multispeed clutch.

Heretofore, in the operation of the draw slide of a mechanical metal drawing press, it has been common to utilize an eccentric or crank movement connected to the draw slide which will cause the draw slide to reciprocate toward and away from the bed of the press at a relatively uniform rate of speed. Depending upon the composition of the metal blank being worked, there is a limit beyond which the speed of the draw can not go without causing a fracture to occur in the work. For example, sheet steel used at the present time has a maximum draw speed of approximately sixty feet per minute. Thus, the draw slide of a press cannot be allowed to reciprocate at a speed greater than sixty feet per minute during the drawing operation, or the sheet metal will not flow properly and will fracture. It is thus evident that with this limitation on the drawing speed of the metal being worked, the output of such a press is limited to the amount of work that can be produced by operating the draw slide at the draw speed of the metal.

However, the production of such a press can be increased without increasing the speed of draw if the speed of the draw slide can be increased in moving from its initial position down to the point of draw and after completion of the daw back to its initial position, but with a reduction in the speed of the draw slide during the actual drawing operation. It is an important object of the present invention to enable such operation of the draw slide of a mechanical metal working press to be accomplished in a novel and expeditious manner.

Another object of our invention is to enable a novel and practical compact multispeed clutch to be afforded for mechanical metal drawing presses, and the like.

In presses, and the like, if a clucth thereof is embedded in the body of the press itself, any breakdown of the clutch may cause the entire press to be shut down while repairs are being made to the clutch. It is another object of the present invention to provide a novel multispeed clutch for use on metal drawing presses, and the like, which may be aiforded in the form of an accessory which may be quickly and easily connected to and disconnected from such a press so that in the event of a breakdown of the clutch the entire clutch may be quickly and easily replaced and the press put back into operation during repairs to the original clutch.

In heavy mechanisms such as, for example, mechanical metal drawing presses, and the like, wherein drive shafts are used for transmitting power, it is not uncommon to have deflection of such shafts. Where gears carried by such a deflected shaft mesh with other gears, which are relatively rigidly mounted on other supporting members such as stationary housings, and the like, misalignment of the gears is caused because of the change in mesh. It is another object of our invention to prevent such misalignment of meshing gears in a novel and expeditious manner.

Yet another object of the present invention is to enable 3,074,297 Patented Jan. 22, 1963 meshing gears to be mounted and supported in a novel and expeditious manner.

A further object of the present invention is to enable a novel multispeed driving mechanism for mechanical metal drawing presses, and the like, to be afforded which embodies a novel intermeshing gear system for transmitting power from, or to, a shaft, and wherein the gear system is movable as a unit radially of the shaft to there by enable the shaft to deflect without changing the alignment of the meshing gears in the system.

Another object of the present invention is to afford a novel multispeed driving mechanism of the aforementioned type which embodies a novel planetary gear systern wherein the ring gear is free-floating in the sense that it is radially movable while still effectively performing its intended functions.

Another object is to afford a novel clutch embodying a novel planetary gear system constituted and arranged in a novel and expeditious manner.

A further object of the present invention is to afford a novel clutch embodying two controls so constituted and arranged as to be effective to drive the shaft at one speed when one control is engaged and the other control is disengaged, and to drive the shaft at another speed when the one control is disengaged and the other control is engaged.

Another object of our invention is to afford a novel clutch of the aforementioned type embodying a novel planetary gear system wherein the ring gear is held against rotation at all times, and the planetary gears and sun gear are continually rotated during operation of the clutch.

Another object ancillary to the foregoing is to enable such a ring gear to be held against rotation in a novel and expeditious manner.

A further object of our invention is to afford a novel multispeed driving mechanism of the aforementioned type which may be operated for prolonged periods of time without becoming overheated.

Another object of our invention is to afford a novel clutch of the aforementioned type which may be readily maintained.

A further object of our invention is to aitord a novel compact clutch for metal drawing presses, and the like, which is effective and efficient in operation and may be readily and economically produced commercially.

Other and further objects of the present invention will be apparent from the following description and claims and are illustrated in the accompanying drawings which, by way of illustration, show the preferred embodiment of the present invention and the principles thereof, and what we now consider to be the best mode in which we have contemplated applying these principles. Other embodiments of the invention embodying the same or equivalent principles may be used and structural changes may be made as desired by those skilled in the art without departing from the present invention and the purview of the an pended claims.

In the drawings:

FIG. 1 is a top plan view of a multispeed driving mechanism embodying the principles of our invention;

FIG. 2 is a fragmentary sectional view taken substantially along the line 22 in FIG. 1;

FIG. 3 is an enlarged fragmentary longitudinal sectional view taken substantially along the plane 3--3 in FIG. 1;

FIG. 4 is a detail sectional view taken substantially along the line 4-4 in FIG. 3;

FIG. 5 is a detail sectional view of the ring gear and the mounting therefor shown in FIG. 4, and taken substantially along the line 5-5 in FIG. 4;

FIG. 6 is a detail sectional view taken substantially 3 along the line 6--6 in FIG. 3, with certain parts broken away to show underlying parts; and

FIG. 7 is a detail sectional view taken substantially along the line 7-7 in FIG. 6.

A multispeed driving mechanism in the form of a two speed clutch 1, embodying the principles of our invention, is shown in the drawings to illustrate a preferred embodiment of the present invention. The clutch 1 shown in the drawings is particularly well adapted for driving the drive shaft of a mechanical metal drawing press, and the like.

In general, the clutch 1 embodies a drive shaft 2 journalled in bearings 3 and 4 in a suitable supporting frame 5, FIGS. 1 and 2. A flywheel 6 and a driven member 7 are journalled on the drive shaft 2, FIGS. 1 and 3, the flywheel 6 comprising the driving member for the clutch 1 and being continuously rotated during operation of the clutch 1. The flywheel 6 is drivingly connected to the driven member 7 by a planetary gear system 8 in a manner which will be discussed in greater detail presently, the driven member 7 rotating at all times during the rotation of the flywheel 6. A high speed clutch 9 and a low speed clutch 10 are mounted on opposite end portions of the drive shaft 2 and are adapted to selectively drivingly connect the flywheel 6 and the driven member 7, respectively, to the drive shaft 2 to thereby selectively drive the shaft 2 at high or low speeds, as will be discussed in greater detail presently.

The drive shaft 2 embodies a front end portion 11 which projects outwardly from the supporting frame 3 and may be connected in any suitable manner to the shaft to be driven by the clutch 1 such as, for example, the drive shaft, for reciprocating the draw slide of a mechanical metal drawing press, or the like, not shown. The clutch 1 is a complete unit which may be connected to any one of several different types of presses, and the like. For example, when desired, the clutch 1 may be mounted on the crown of a press, with the shaft 2 suitably connected to the drive shaft of the press. In other instances, it may be desirable to mount the clutch 1 on the floor beside such a press, or to mount the clutch 1 in elevated position on a suitable platform, or the like, projecting outwardly from the side of a press. In any event, it will be seen that with our novel clutch 1, the clutch may always be connected to a metal working press, or the like, in the form of an outwardly disposed accessory which may be readily removed from the press, as a unit, so that in the event of a breakdown of the clutch, the entire clutch may be quickly and easily removed and replaced so that the press may again be placed in operation during repair of the clutch.

Referring now more particular to the drawings, it will be seen that the flywheel 6 embodies a relatively massive body member 12 having bosses 13 projecting forwardly from the front face thereof, FIGS. 1 and 3. A front end plate member 14 is secured to the body member 12 in juxtaposition to the front end of the bosses 13 by studs 15. The flywheel 6 also embodies a rearwardly projecting centrally disposed hub 16 which is journalled on the shaft 2, FIG. 3.

A sun gear 17 is mounted on and keyed to the hub 16, FIGS. 3 and 4. A plurality of planetary gears 18 are mounted on shafts 19 journalled in a suitable carrier 20, which forms a forwardly projecting hub portion of the driven member 7.

The driven member 7 embodies a body member 21 having bosses 22 extending rearwardly from the outer peripheral edge portion of the rear face thereof, FIGS. 3 and 6. A rear end plate member 23 is secured by studs 24 to the body member 21 in juxtaposition to the rear faces of the bosses 22. The front and rear end portions of the carrier are rotatably mounted on the hub 16 of the flywheel 6 by suitable bearings 25 and 26, respectively, FIG. 3. It will be remembered that the carrier 20 affords a forwardly projecting hub portion of the driven member 7 and, therefore, it will be seen that the driven member 7 is rotatably mounted on and supported by the hub portion 16 of the flywheel 6.

A ring gear 27 is disposed around the planetary gears 18 in meshing engagement therewith, FIGS. 3 and 4. The ring .gear 27 is annular in shape except that it has two diametrically opposed, substantially rectangularshaped cars 28 and 29 projecting radially outwardly from the upper and lower peripheral edge portions thereof, respectively, FIGS. 3, 4 and 5. The ring gear 27 is mounted in an outer ring 30 which has an inside diameter which is slightly larger than the outside diameter of the ring gear 27, FIGS. 4 and 5.

The outer ring 30 has four outwardly projecting cars 31, 32, 33 and 34, with the cars 32 and 34 being diametrically opposed and projecting radially outwardly from the upper and lower peripheral edge portions of the outer ring 30, respectively, and with the cars 31 and 33 being diametrically opposed and projecting radially outwardly in opposite horizontal directions from the outer peripheral edge of the outer ring 30.

The outer ring 30 has two diametrically opposed inwardly opening slots 35 and 36 extending laterally therethrough, the slots 35 and 36 extending radially into the ears 32 and 34, respectively, FIG. 4. The slots 35 and 36 are of such size, and are so positioned on the outer ring 30 that when the ring gear 27 is disposed in the outer ring 30, the ears 28 and 29 on the ring gear 27 are disposed in the slots 35 and 36, respectively. The slots 35 and 36 are somewhat deeper than the length of the ears 28 and 29, but are of such width that the lateral sides of the ears 28 and 29 engage the sides of the slots 35 and 36, respectively, with a relatively snug sliding fit. Hence, it will be seen that when the ring gear 27 is mounted in the outer ring 30, the ring gear 27 may move upwardly and downwardly relative to the outer ring 30, but is held against rotation, or horizontal lateral movement, relative to the outer ring 30 by the engagement of the cars 28 and 29 in the slots 35 and 36.

Two compression coil springs 37 and 38 are mounted in openings 39 and 40 in the cars 32 and 34, respectively, of the outer ring 30 and project inwardly therefrom into engagement with the outer end portions of the cars 28 and 29, respectively, of the ring gear 27. The compression springs 37 and 38 are held in such position in the openings 39 and 40 by suitable means such as, for example, plugs 41 and 42 secured in the outer end portions of the openings 39 and 40, respectively, that the inner ends of the springs 37 and 38 are held in yielding engagement with the outer ends of the cars 28 and 29 in the ring gear 27. The springs 37 and 38 are of such strength that the ring gear 27 is normally supported thereby in centered position within the outer ring 30, from which normal position the ring gear 27 may be moved upwardly or downwardly in the outer ring 30 against the urging of the springs 37 and 38.

The cars 31-34 on the outer ring 30 are mounted in channel-shaped brackets 43, 44, 45 and 46, respectively, which are secured to a Wall member 47 of the stationary housing 48 of the clutch 1, FIGS. 3, 4 and 5, by bolts 49 in position to enclose the ears 31-34 between the wall member 47 and the brackets 43-46, respectively. The ears 31 and 33 and the brackets 43 and 45 are of such size that the cars 31 and 33 fit relatively snugly with a free sliding fit, between the side wall portions of the brackets 43 and 45. The ears 32 and 34 and the brackets 44 and 46 are of such size that the ears 32 and 34 fit relatively loosely in the brackets 44 and 46 so that the cars 32 and 34 may move laterally in a horizontal direction, to the left and right, as viewed in FIG. 4, relative to the brackets 44 and 46. With this construction, the outer ring 30 is held against rotation and upward and downward movement, relative to the housing 48, by the engagement of the ears 31 and 33 with the brackets 43 and 45, but is free to slide a limited amount horizontally relative to the housing 48, the cars 31 and 33 being slidable longitudinally in the brackets 43 and 45 and there being clearance between the ears 32 and 34 and the brackets 44 and 46 to permit such horizontal movement of the outer ring 38 relative to the housing 48.

It will be remembered that the ring gear 27 is movable upwardly and downwardly relative to the outer ring 36. Hence, with the ring gear 27 so mounted relative to the outer ring 30, and with the outer ring 30 mounted for horizontal movement relative to the wall member 47 of the housing 48, it will be seen that the ring gear 27 is radially movable in all directions so that it floats in the housing 48, although it is held against rotation relative thereto.

Hence, it will be seen that with the ring gear 27 floatingly mounted in the housing 48 and with the sun gear 17 and the planetary gears 18 both carried by, and laterally movable with, the shaft 2, our novel planetary gear system 8 is so constituted and arranged that, if during operation of the clutch 1, the shaft 2 is deflected, the panetary gear system 8 may also deflect, as a unit, so as to prevent misalignment of the gears 17, 18 and 27.

When the ring gear 27 is so mounted in the outer ring 30, it is held against axial movement relative to the outer ring 30 by two clamping rings 50 and 51 which are disposed on opposite sides of the outer ring 30, and are held in juxtaposition thereto by suitable means such as bolts 52, FIGS. 4 and 5. The rings 50 and 51 project radially inwardly from the outer ring 30 a suflicient distance that they are disposed in overlying relation to the outer peripheral edge of the ring gear 27 in position to hold the ring gear 27 against axial movement relative to the outer ring 30.

Hence, it will be seen that during rotation of the flywheel 6, the latter is effective through the connection of its sun gear 17 with the planetary gears 18, to rotate the carrier 20 and, therefore, the driven member 7 in the same direction as the flywheel 6 but at a reduced rate of speed. Therefore, it will be seen that by selectively coupling the drive shaft 2 to the flywheel 6 and the driven member 7, during rotation of the flywheel 6, the drive shaft 2 may be selectively driven at a high or low rate of speed. To effect this selective coupling of the flywheel 6 and the driven member 7 to the drive shaft 2, we have afforded the high speed clutch 9 and the low speed clutch 10, respectively, which will now be discussed in greater detail.

The low speed clutch embodies a driving member 53 and a driven member 54, FIG. 3. The driven member 54 embodies a substantially flat annular-shaped plate 55, having a centrally located rearwardly projecting hub 56. The driven member 54 is mounted on the shaft 2 in such position that the plate 55 is disposed forwardly of the rear end plate 23 of the driven member 7, the plate 55 being of such diameter that it fits freely between the bosses 22 of the driven member 7 in inwardly spaced relation thereto, FIGS. 3 and 6. The hub 56 of the driven member 54 projects rearwardly from the plate 55 outwardly through an opening 57 in the rear end plate 23 of the driven member 7, FIG. 3. The driven member 54 is secured to the shaft 2 for rotation therewith by suitable means such as a key 58, and is held against rearward movement on the shaft 2 by a locknut 59 threaded onto the shaft 2, FIGS. 1 and 3.

The plate 55 of the low speed clutch 10 has a plurality of round openings 60 extending therethrough in spaced relation therearound, FIGS. 3 and 4. Friction members 61 are mounted in the openings 60 and project laterally outwardly therefrom for a purpose which will be discussed in greater detail presently. Each of the friction members 61 embodies a circular-shaped, substantially flat plate or body member 62 mounted in a ring 63. The body member 62 may be made of any suitable material such as, for example, aluminum, and the ring 63 preferably has an inwardly projecting rib 64 so that the body member 62 is secured against lateral displacement from the ring 63, FIGS. 3, 6 and 7. Two circular-shaped discs or lining members 65 and 66 made of suitable friction material, and which are of the same diameter as the body member 62, are secured to the opposite faces of the body member 62, in juxtaposition thereto, by suitable means such as, for example, a suitable binder or adhesive.

The plate 55 has a plurality of openings 67 extending laterally therethrough, each of the openings 67 projecting radially inwardly from a respective one of the openings 60. Each of the friction members 61 has an opening 68 extending diametrically through the body member 62 and outwardly through one side of the ring 63. The friction members 61 are of such size that they may be readily moved laterally into and out of the openings 60 in the plate 55. Pins 69 having enlarged heads 70 on one end thereof may be inserted into the openings 68 in the friction member 61 with the heads 70 disposed outwardly of the ring 63. The heads 70 are of such size that when the friction members 61 are moved laterally into the openings 60 in the plate 55, the heads 70 may be moved laterally inwardly into the respective openings 67 adjacent the respective openings 60 with a snug fit so that the pins 69 are effective to hold the friction members 61 against rotation relative to the plate 55.

The driving member 53 of the low speed clutch 10 embodies a substantially annular-shaped piston 71 slidably mounted on a sleeve 72 journalled on the shaft 2. The sleeve 72 forms a part of the driven member 7 and projects rearwardly toward the driven member 54 of the low speed clutch 10, FIG. 3. The piston 71 embodies a plurality of radially outwardly projecting cars 73 spaced around the periphery thereof, the cars 73 being disposed between, and spaced peripherally from, adjacent pairs of the bosses 22 on the driven member 7, FIGS. 3 and 6. A plurality of bolts 74, having threads 75 formed on one end thereof and an enlarged head 76 formed on the other end thereof, extend through the ears 73 on the piston 71 with the forward threaded end portion 75 thereof threadedly engaged in the driven member 21, and with the heads 76 projecting rearwardly from the cars 73 in radially outwardly spaced relation to the plate 55 of the driven member 54 of the clutch 10, FIG. 3. Compression coil springs 77 are mounted on the bolts 74 between the heads 76 thereof and the ears 73 in position to yieldingly urge the piston 71 forwardly on the shaft 2, away from the driven member 54. Hence, it will be seen that the piston 71 is secured to the driven member 7 for rotation therewith, but is axially slidable relative thereto.

The driven member 7 embodies an annular recess or chamber 78 formed in the body member 21 forwardly of the piston 71, FIG. 3. A diaphragm 79 is mounted on the driven member 7 in covering relation to the'chamber 78 and is secured to the driven member 7 by suitable means such as the sleeve 72 and a clamping ring 80, em gaged with the radial outer and inner edge portions, the diaphragm 79, the sleeve 72 and the ring 80 being held in position to clamp the aforementioned respective edge portions of the diaphragm 79 against the body portion 21 of the driven member 7 by suitable means such as bolts 81 and 82, respectively, FIG. 3.

Air passages 83 extend through the sleeve 72 and the inner edge portion of the diaphragm 79, and are in communication at one end with the chamber 78 and at the now Patent Number 3,021,146, the air seal shown in the drawings embodying a passageway 86, which is in communication at one end with a chamber 84 and atv the other end with a passageway 87 extending radially outwardly through the shaft 2 from an air passageway 88 extending longitudinally through the rear end portion of the shaft 2.

It will be seen that with this construction air may be fed under pressure through the passageway 88, as will be discussed in greater detail presently, and thence through the passageway 87, the air seal 85, and the passageway 83 into the chamber 78 to thereby bulge the diaphragm 79 rearwardly, or to the right as viewed in FIG. 3. Such movement of the diaphragm 79 is effective to move the piston 71 rearwardly against the urging of the springs 77 to thereby press the rear face 89 of the piston 71 against the linings 65 of the friction members 61. Such movement of the piston 71 is effective to slide the friction members 61 rearwardly through the openings 60 in the plate 55 of the low speed clutch member and thereby press the rear face of the linings 66 of the friction members 61 into engagement with the front face 90 of the rear end plate 23 of the driven member 7.

It will be remembered that the driven member 7, including the piston 71 and the rear end plate 23, are constantly rotating during rotation of the flywheel 6, although at a lower rate of speed than the flywheel 6 and, therefore, clamping of the friction members 61 between the piston 71 and the rear end plate 23 is effective to drivingly connect the driven member 7 to the shaft 2, the driven member 54 of the clutch 10 being keyed to the shaft as previously discussed.

The high speed clutch 9 is identical in construction to the low speed clutch 10 and the parts thereof are indicated in the drawings by the same reference numerals as those indicating the corresponding parts of the low speed clutch 10. In the high speed clutch 9, the piston 71 of the driven member 53 thereof is mounted on a sleeve 72 which is connected to and rotatable with the body member 12 of the flywheel 6. The bolts 74 which extend through the ears 73 of the high speed clutch 9 have their threaded end portions 75 threadedly engaged in the body member 12 of the flywheel 6, and are disposed between the bosses 13. A chamber 91, like the chamber 78 in the driven member 7, is formed in the rear face of the body member 12 of the flywheel 6, and the diaphragm 79 of the high speed clutch .9 is clamped against the body member 12 in covering relation .to the chamber 91 by the sleeve 72 and the ring 80 on the flywheel 6, the latter being held on the body member 12 by suitable bolts 81 and 82, respectively. The sleeve 72 on the flywheel 6 is mounted on an air seal 85, and the chamber 91 is connected by a passageway 83 to the chamber 84 in the last mentioned air seal 85. The passageway 86 of the air seal 85 of the high speed clutch 9 is connected by a radially outwardly extending passageway 92 in the shaft 2 tea passageway 93 which extends rearwardly therefrom longitudinally through .the shaft 2 in parallel relation to the low speed clutch air passageway 88.

When air is fed under pressurethrough the passageway 93, the passageway 92, the high speed clutch air seal 85, the passageway 83, into the chamber 91, the diaphragm 79 in the high speed clutch 9 is' bulged forwardly to thereby move theassociated piston 71 forwardly and clamp the friction members 61 of the high speed clutch 9 between the last mentioned piston 71 and the rear face 94 of the front end plate 14 ofthe flywheel 6 to thereby drivingly connect the flywheel 6 to the shaft 2, the hub 56 of the clutch 9 projecting forwardly through an opening 95 in the end plate 14 and being connected to the drive shaft 2. by suitable means such as a key 96.

Hence, it will be seen that when the flywheel 6 is being rotated by suitable driving means, not shown, as previously discussed, the shaft 2 may be either directly connected to the flywheel 6 for rotation therewith at high speed, or may be directly connected to the driven member 21 for rotation therewith at low speed. This'selective connecting, of the shaft 2 to, the flywheel 6 orthedriven member 21 may be effected by selectively operating the clutches 9 and 10. When it is desired to drive the shaft 2 at high speed the high speed clutch 9 may be engaged and the low speed clutch 10 disengaged. When, on the other hand, it is desired to drive the shaft 2 at low speed, the low speed clutch 10 may be engaged and the high speed clutch 9 may be disengaged.

It has been found that with the parts of a multispeed driving mechanism constituted and arranged in the mannor of the parts of our novel multispeed driving mechanism, a compact, practical and etficient multispeed clutch is afforded which may be used to quickly and easily change the speed of operation of even relatively massive machines such as, for example, large mechanical metal drawing presses, and the like.

Also, it has been found that with this construction friction members 61 of the clutches 9 and 10, and the parts frictionally engaged thereby when the clutches 9 and 10 are actuated, are subjected to remarkably little wear and that the clutches 9 and 10 enjoy a long life.

Also, it has been found that with the driven member 7 connected to the flywheel 6 in the novel manner disclosed herein, the novel planetary gear system 8 is subjected to little weaneven when the drive shaft 2 is used for actuating the aforementioned relatively massive Inachines.

In addition, it has been found that with the novel two speed clutch 1 constructed in the manner disclosed herein, it lends itself to ready and effective lubrication of the parts thereof. Such lubrication may be effected through an oil system which includes an oil passageway 97 extending longitudinally through the rear end portion of the shaft 2, with other passageways such as the passageways 98 extending radially outwardly therefrom through the shaft 2 into communication with passageways such as the passageways 99 afforded in the parts of the multispeed driving mechanism 1 mounted on the shaft 2, FIG. 3.

The compressed air or other working fluid fed through the passageways 88 and 93 to actuate the low speed clutch 10, and the high speed clutch 9, respectively, and the oil fed through the passageway 98 to lubricate the high speed driving mechanism 1, may be fed from any suitable source of supply, not shown, through suitable conduits such as pipes 100, 101 and 102, respectively, and a suitable coupling member, such as, for example, a rotary union 103, FIG. 1, into the rear end portion of the shaft 2.

From the foregoing it will be seen that we have afforded a novel and practical multispeed driving mechanism which is particularly well adapted for driving heavy machinery such as, for example, large mechanical metal drawing presses, and the like.

Also, it will be seen that we have afforded a novel, practical, and eflicient multispeed driving mechanism which may be readily and economically produced commercially, and which may be quickly and easily connected to and disconnected from machines which are to be driven thereby.

Thus, while we have illustrated and described the preferred embodiment of our invention, it is to be understood that this is capable of variation and modification, and we therefore do not wish to be limited to the precise details set forth, but desire to avail Ourselves of such changes and alterations as fall within the purview of the appended claims.

We claim:

1. A multispeed driving mechanism for a driven shaft comprising driving means rotatably mounted on such a shaft for rotation therearound, driven means rotatably mounted on said driving means and said shaft and operatively connected to said driving means for rotation by said driving means and around said driving means during all rotation of the latter, and clutch means for selectively connecting said shaft to said driven means and said driving means, and said clutch means including two friction means mounted on said shaft on opposite sides of said driving means for rotation with said shaft, one of said friction means being operatively engageable with said driving means for drivingly connecting said driving means to said shaft, the other of said friction means being operatively engageable with said driven member for drivingly connecting said driven member to said shaft.

2. In a multispeed driving mechanism for a driven shaft comprising driving means rotatably mounted on such a shaft for rotation therearound, driven means rotatably mounted on said driving means and said shaft and operatively connected to said driving means for rotation by and around said driving means during all rotation of the latter, two friction members mounted on and carried by said shaft on opposite sides of said driving means for rotation with said shaft, said friction members being independently engageable with said driving means and said driven means, respectively, for rotation thereby to thereby rotate said shaft.

3. A multispeed driving mechanism comprising a shaft, normally constantly rotating driving means journalled on said shaft, driven means rotatably mounted on said driving means and operatively connected thereto for constant rotation by and relative to said driving means at a slower rate of speed than that of said driving means during all rotation of the latter, two friction members mounted on said shaft and projecting outwardly therefrom into position to be moved into operative engagement with said driving means and driven means, respectively, and fluid actuated means for moving said friction members into engagement with said driving means and driven means, respectively, to thereby selectively connect said shaft to said driving means and said driven means for rotation thereby.

4. A multispeed driving mechanism comprising a rotatable shaft, driving means journalled on said shaft and including a hub portion, and a sun gear mounted on and rotatable with said hub portion, driven means journalled on and supported by said hub portion on two sides of said sun gear, said driven means including planetary gears disposed radially of and operatively engaged with said sun gear for rotation by the latter, a ring gear operatively engaged with said planetary gears, means holding said ring gear against rotation, and clutch means operable to selectively drivingly connect said driving means and said driven means to said shaft.

5. A multispeed driving mechanism comprising a rotatable shaft, driving means journalled on said shaft and including a hub portion, and a sun gear mounted on and rotatable with said hub portion, driven means journalled on and supported by said hub portion, said driven means including planetary gears disposed radially of and operatively engaged with said sun gear for rotation by the latter, a ring gear operatively engaged with said planetary gears, means holding said ring gear against rotation, two friction members mounted on said shaft and connected thereto for rotation therewith, said friction members projecting radially outwardly from said shaft and being movable longitudinally thereof into and out of connecting engagement with said driving means and said driven means, respectively, and means for independently moving said friction members into said connecting engagement to thereby selectively connect said shaft to said driving means and said driven means for rotation thereby.

6. A multispeed driving mechanism comprising a rotatable shaft, driving means journalled on said shaft and including a hub portion, and a sun gear mounted on and rotatable with said hub portion, driven means journalled on and supported by said hub portion, said driven means including planetary gears disposed radial-1y of and operatively engaged with said sun gear for rotation by the latter, a ring gear operatively engaged with said planetary gears, means holding said ring gear against rotation, two friction members mounted on said shaft and connected thereto for rotation therewith, said friction members projecting radially outwardly from said shaft and being movable longitudinally thereof into and out of connecting engagement with said driving means and said driven means, respectively, and means, including diaphragms carried by said driving means and said driven means operable to independently move said friction members into said connecting engagement to thereby selectively drivingly connect said driving means and said driven means to said shaft.

7. A multispeed driving mechanism comprising supporting means, a ring gear mounted on and carried by said supporting means, a shaft extending through said ring gear and journalled in and carried by said supporting means for rotation relative to the latter, driving means journalled on said shaft and including a hub portion disposed in said ring gear, and a sun gear mounted on and secured to said hub portion for rotation within said ring gear, driven means journalled on said shaft and including another hub portion disposed in said ring gear and journalled on said first mentioned hub portion, and planetary gears journalled on said other hub portion and operatively connected to said sun gear and said ring gear for rotation internally around said ring gear during rotation of said sun gear, and clutch means for connecting said driving means and said driven means to said shaft during rotation of said driving means and said driven means.

8. In a multispeed driving mechanism comprising a supporting means, a ring gear mounted on and carried by said supporting means, a shaft extending through said ring gear and journalled in and carried by said supporting means for rotation relative to the latter, a flywheel journalled on said shaft and including a hub portion disposed in said ring gear, and a sun gear mounted on and fixed to said hub portion Within said ring gear, driven means including another hub portion disposed in said ring gear and journalled on said first mentioned hub portion, and planetary gears journalled on said other hub portion and operatively connected to said sun gear and said ring gear for rotation internally around said ring gear during rotation of said sun gear, friction means projecting radially outwardly from said shaft into said flywheel, and other friction means projecting radially outwardly from said shaft into said driven means, both said friction means being connected to said shaft for rotation therewith, said first mentioned friction means and said other friction means being selectively movable axially of said shaft into operatively connecting engagement with said flywheel and said driven means, respectively, to thereby selectively connect said shaft to said flywheel and said driven means for rotation thereby.

9. A multispeed driving mechanism comprising a supporting means, a ring gear mounted on and carried by said supporting means, a shaft extending through said ring gear and journalled in and carried by said supporting means for rotation relative to the latter, driving means journalled on said shaft and including a hub portion disposed in said ring gear, and a sun gear mounted on and fixed to said hub portion within said ring gear, driven means including another hub portion disposed in said ring gear and journalled on said first mentioned hub portion, and planetary gears journalled on said other hub portion and operatively connected to said sun gear and said ring gear for rotation internally around said ring gear during rotation of said sun gear, friction means projecting radially outwardly from said shaft into said driving means, other friction means projecting radially outwardly from said shaft into said driven means, both said friction means being connected to said shaft for rotation therewith, diaphragms mounted in and carried by said driving means and said driven means in position to move said first mentioned friction means and said other friction means, upon actuation thereof, into connecting engagement with said driving means and said driven means, respectively, said shaft having passageways therein for feeding working fluid through said shaft into said driving means and said driven means into position to move said diaphragrns and thereby actuate said first mentioned friction means and said other friction means, respectively.

10. In a multispeed driving mechanism for a metal working press, or the like, and which includes stationary supporting means, and two rotatable driving members, one of said driving members being driven by the other of said driving members: a sun gear mounted on and carried by said other driving member, planetary gears mounted on and carried by said one driving member, said planetary gears being spaced around and meshed with said sun gear, a ring gear extending around said planetary gears and meshed therewith, said ring gear having two radially outwardly projecting diametrically opposed ears thereon, a ring having two perpendicularly disposed pairs of radially outwardly extending diametrically opposed ears thereon,

each of the ears in one of said pairs each having a radially.

inwardly opening recess therein, said ring gear being mounted in said ring with said first mentioned ears disposed in respective ones of saidrecesses in close fitting slidable relation thereto whereby said ring gear is movable relative to said ring along said first mentioned diameter and is held against rotation relative to said ring, spring means in said recesses and engaged with said first mentioned ears in position to yieldingly support said ring gear in centered position in said ring, and means including two brackets on said supporting means for supporting said ring, each of said two brackets engaging a respective one of said ears of the other pair of ears on said ring in position'to movably support said ring on said supporting means in position to hold said ring against rotation relative thereto and to permit sliding movement of said ring References Cited in the file of this patent UNITED STATES PATENTS 1,342,195 Walker June 1, 1920 1,863,110 Salerni June 14, 1932 2,331,684 Henningsen Oct. 12 1943 2,472,788 Burrus June 14, 1949 2,693,722 Winther Nov. 9, 1954 2,727,601 Shurts n Dec. 20, 1955 2,775,330 Schjolin et al. Dec. 25, 1956 2,844,052 Stoeckicht July 22, 1958 2,903,110 Moody Sept. 8, 1959 2,924,983 Curran Feb. 16, 1960 FOREIGN PATENTS 148,273 Great Britain Aug. 8, 1921 107,032 Sweden Apr. 6, 1943 1,097,713

France July 8, 1955 

1. A MULTISPEED DRIVING MECHANISM FOR A DRIVEN SHAFT COMPRISING DRIVING MEANS ROTATABLY MOUNTED ON SUCH A SHAFT FOR ROTATION THEREAROUND, DRIVEN MEANS ROTATABLY MOUNTED ON SAID DRIVING MEANS AND SAID SHAFT AND OPERATIVELY CONNECTED TO SAID DRIVING MEANS FOR ROTATION BY SAID DRIVING MEANS AND AROUND SAID DRIVING MEANS DURING ALL ROTATION OF THE LATTER, AND CLUTCH MEANS FOR SELECTIVELY CONNECTING SAID SHAFT TO SAID DRIVEN MEANS AND SAID DRIVING MEANS, AND SAID CLUTCH MEANS INCLUDING TWO FRICTION MEANS MOUNTED ON SAID SHAFT ON OPPOSITE SIDES OF SAID DRIVING MEANS FOR ROTATION WITH SAID SHAFT, ONE OF SAID FRICTION MEANS BEING OPERATIVELY ENGAGEABLE WITH SAID DRIVING MEANS FOR DRIVINGLY CONNECTING SAID DRIVING MEANS TO SAID SHAFT, THE OTHER OF SAID FRICTION MEANS BEING OPERATIVELY ENGAGEABLE WITH SAID DRIVEN MEMBER FOR DRIVINGLY CONNECTING SAID DRIVEN MEMBER TO SAID SHAFT. 